JP2006144636A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas compressor capable of operating a check valve arranged in a suction port smoothly and lightly. <P>SOLUTION: The suction port 14 for sucking refrigerant gas G from the outside is formed on a discharge chamber 15 side, and a suction passage 70 for communicating the suction port 14 with a suction chamber 13 is formed in a case 11. Gas discharging passages 71, 72 for communicating a space S1 on a compression side of the check valve 60 provided in the suction port 14 with the suction passage 70 are formed to let internal pressure in the space S1 on the compression side when sucking refrigerant gas G escape into the suction passage 70. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a gas compressor, and more particularly to improvement in the movement of a check valve in a gas compressor in which a suction port is provided on a side closer to a discharge chamber with respect to a compressor body.

  Conventionally, air compressors for compressing refrigerant gas and circulating the refrigerant gas through the system have been used in air conditioning systems (hereinafter referred to as air conditioning systems).

  As this gas compressor, a reciprocating type or a rotary type has been put to practical use as an operation method. As the rotary type gas compressor, for example, the one shown in FIG. 4 is known. The illustrated gas compressor is a vane rotary type compressor 100, which rotates by obtaining a driving force from external power, a rotating shaft 51 that rotates integrally with the rotating shaft 51, and a rotor. 50, the cylinder 40 covering the outer periphery of the outer periphery 50, two side blocks (the front side block 20 and the rear side block 30) sandwiching the rotor 50 from both end surfaces of the rotor 50, and the inner periphery of the cylinder 40 from the rotor 50 A compressor main body including a plurality of vanes 58 that can project in the surface direction, and the suction port 14 that covers the outside of the compressor main body and from which the refrigerant gas G (gas) is sucked from the outside and the outside The housing 10 is formed with a discharge port 16 through which the refrigerant gas G is discharged.

  Here, the housing 10 covers a case 11 that wraps substantially the entire compressor body, and an outer side of the front side block 20 side, and an electromagnetic clutch 90 that applies a rotational driving force to the rotary shaft 51 is rotatably attached. The compressor main body is housed in an internal space that includes the front head 12 and is partitioned by the case 11 and the front head 12.

  Further, with respect to the axial direction of the rotating shaft 51, the suction port 14 is located on the side of the compressor body with the outer surface of the front side block 20 and the inner surface of the front head 12, and communicates with the compressor body. A suction chamber 13 into which the refrigerant gas G to be sucked is introduced is formed, and communicates with the suction port 16 by the outer surface of the rear side block 30 and the inner surface of the case 11 on the side of the discharge port 16 across the compressor body. A discharge chamber 15 in which the refrigerant gas G discharged from the compressor body is stored is formed.

  An oil separator (such as a wire mesh) 82 that separates the refrigerating machine oil R mixed in the refrigerant gas G discharged from the compressor main body from the refrigerant gas G inside the discharge chamber 15 and on the outer surface of the rear side block 30. The cyclone block 80 provided with is fixed.

  The refrigerating machine oil R separated by the oil separator 82 accumulates at the bottom of the discharge chamber 15, passes through the oil passage 31 drilled from the bottom of the rear side block 30 to the bearing of the rotary shaft 51, and is a bearing portion of the rear side block 30. On the other hand, the bearing portion of the front side block 20 is lubricated through the oil passage 31 of the rear side block 30, the oil passage 46 formed in the cylinder 40, and the oil passage 21 formed in the front side block 20.

  Further, the refrigerating machine oil R that reaches the bearing portions of the front side block 20 and the rear side block 30 and is pumped in the direction of the rotor 50 through a minute gap between the rotary shaft 51 is a vane groove formed in the rotor 50. 56 (see the sectional view of FIG. 4B).

  Here, five vane grooves 56 are formed at equal angular intervals in the circumferential direction of the rotor 50, and each vane groove 56 has a width substantially equal to the axial length of the rotor 50. A vane 58 that can project from the outer peripheral surface of the rotor 50 toward the inner peripheral surface 49a of the cylinder 40 is provided.

  A vane back pressure chamber 59 is formed by the end surface of the vane 58 on the center side of the rotor 50 and the wall surface of the vane groove 56, and the refrigerating machine oil R reaching the vane groove 56 applies an internal pressure to the vane back pressure chamber 59. By hanging, the vane 58 protrudes from the outer peripheral surface of the rotor 50 toward the inner peripheral surface 49 a of the cylinder 40.

  Thus, each vane 58 protrudes, and the tip of each vane 58 on the radially outer side of the rotor 50 abuts on the inner peripheral surface 49a of the cylinder 40, whereby the outer peripheral surface of the rotor 50, the inner peripheral surface of the cylinder 40, and The internal space of the compressor body surrounded by the both side blocks 20 and 30 forms five compression chambers 48 whose volumes change as the rotor 50 rotates.

  In FIG. 4A, reference numeral 18 denotes a lip seal, and in FIG. 4B, reference numeral 44 denotes a discharge chamber, reference numeral 43 denotes a discharge valve, and reference numeral 42 denotes a compression chamber 48 and a discharge chamber in the final stage of the compression stroke. The discharge valve 43 is configured by a valve main body 43a and a valve support 43b. Further, reference numeral 34 in FIG. 4B is a discharge passage formed in the rear side block 30 for guiding the refrigerant gas G from the discharge chamber 44 to the oil separator 82 formed in the rear side block 30.

  Here, as shown in FIG. 5, the suction port 14 allows the refrigerant gas G (and the mixed refrigerating machine oil R) to be sucked into the compressor 100 from the outside to the inside, and from the inside of the compressor 100 to the outside. A check valve 60 for preventing the backflow of the refrigerant gas G (and the mixed refrigerating machine oil R) is provided.

  The check valve 60 has a substantially cylindrical sleeve 65 in which one end (upper end in the figure) is opened and a suction opening 65 a communicating with the suction chamber 13 is formed in a peripheral wall thereof. A valve body 63 that is slidable along the axial direction of the cylindrical shape and divides the internal space of the sleeve 65 into two spaces with respect to the axial direction of the sleeve 65, and the valve body 63 in the direction of the upper end of the sleeve 65. A helical spring 64 (biasing means) for biasing and a stopper 61 for restricting the upward movement of the valve body 63 at the upper end of the sleeve 65 are provided, and a bottom plate 65b which is the other end of the sleeve 65 is provided on the bottom plate 65b. Is formed with an oil drain hole 65c for discharging the refrigerator oil R.

  As shown in FIG. 5A, the check valve 60 is configured such that the stopper 61 and the valve body 63 are in contact with each other when the valve body 63 is biased toward the upper end opening side of the sleeve 65. The refrigerant gas G and the refrigerating machine oil R are prevented from being discharged from the suction chamber 13 to the outside of the compressor 100. On the other hand, when the refrigerant gas G is supplied from the outside, due to the pressure balance between the outside and the inside, When the valve body 63 is pushed down against the urging force of the helical spring 64 and the skirt portion 63a of the valve body 63 is lowered from the suction opening 65a, as shown in FIG. G passes through the suction opening 65a and is supplied to the suction chamber 13.

  At this time, among the internal space of the sleeve 65, a space S1 on the lower side of the valve body 63 in the figure is a compression side space (Patent Document 1).

  By the way, the above-described compressor 100 is a general one in which the suction port 14 is provided close to the suction chamber 13. However, depending on the arrangement space and orientation of the compressor or the specifications of the connecting pipe to the compressor, the suction port 14 may be used. In some cases, the port 14 cannot be provided close to the suction chamber 13 but rather is provided close to the discharge chamber 15.

  That is, for example, the compressor 100 shown in FIG. 6 has the suction port 14 provided on the discharge chamber 15 side, and the discharge port 16 is provided in the illustrated depth direction of the suction port 14. Since the pipes connected to 14 and 16 can be adjacent to each other, the pipe connection workability is improved.

In the illustrated compressor 100, in order to supply the refrigerant gas sucked from the suction port 14 on the discharge chamber 15 side to the suction chamber 13 located on the side opposite to the discharge chamber 15, A suction passage 70 extending substantially parallel to the rotation shaft 51 is provided (outward in the radial direction around the rotation shaft 51).
JP 2002-257046 A

  In the compressor 100 configured as described above, it is necessary to provide a check valve 60 at the suction port 14 as shown in the figure. However, the compressor 100 shown in FIG. 6 is adjacent to the suction chamber 13, the compressor 100 shown in FIG. 6 has a relatively long suction passage 70 between the suction port 14 and the suction chamber 13. There is a possibility that energy loss of ventilation by the suction passage 70 occurs, and the suction efficiency into the suction chamber 13 is lowered.

  For this reason, when the refrigerant gas G is sucked, the check valve 60 is largely opened to suppress the ventilation resistance in the check valve 60, so that the energy loss generated in the suction passage 70 is reduced to the energy loss in the check valve 60. It is conceivable to compensate for this by reducing the energy loss of the entire intake system.

  However, when the check valve 60 is largely opened, it is necessary to increase the stroke amount of the valve body 63. When the stroke amount is increased, when the check valve 60 is opened, A compression pressure acts on one space (lower space in FIG. 6) S1 partitioned by the valve body 63.

  As a result, when the check valve 60 is opened, the valve body 63 receives a reaction force from the compression-side space S1 in a direction (upward in the figure) opposite to the displacement direction (downward in the figure). There may be a problem that the smooth and light operation of 63 is hindered.

  If the check valve 60 cannot perform the intended operation, as described above, the energy loss of the suction system increases and the efficiency of the compressor 100 is reduced.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas compressor that can make the operation of a check valve disposed in a suction port smooth and light. .

  In the gas compressor according to the present invention, the compression pressure generated in the compression-side space is such that the space on the compression side in the gas suction operation of the check valve communicates with the suction passage connecting the suction port and the suction chamber. The check valve is operated smoothly and lightly by allowing the air to escape to the intake system.

  That is, the gas compressor according to the present invention includes a compressor body having a rotating body that rotates about a rotation axis, an outer side of the compressor body, a suction port through which gas is sucked from the outside, and a gas to the outside And a housing formed with a discharge port for discharging gas, and communicated with the suction port, into which a gas sucked into the compressor body is introduced, and communicated with the discharge port and discharged from the compressor body. A discharge chamber in which the stored gas is stored is formed with the compressor body in between with respect to the axial direction of the rotating shaft, and the suction port allows the gas to be sucked from the outside to the inside, and the gas from the inside to the outside In a gas compressor provided with a check valve for preventing backflow, a suction port is formed on the discharge chamber side in the axial direction, and a suction passage is formed in the housing to connect the suction port and the suction chamber. valve , And space to be compressed side in the suction operation of the gas, the gas vent passage for communicating the suction passage, characterized in that it is formed in the housing.

  Here, the suction port is formed on the discharge chamber side with respect to the axial direction. The suction port is formed at a portion closer to the discharge chamber than the suction chamber with respect to the extending direction of the rotating shaft. Means.

  According to the gas compressor according to the present invention configured as described above, during the gas suction operation of the check valve, the gas (refrigerant gas or the like) or the lubricating oil (refrigerator oil) occupying the compression side space of the check valve. Etc.) is released to the suction passage through the gas vent passage communicating with the compression side space, and the reaction force that the check valve receives from the compression side space can be greatly reduced. The check valve can be operated smoothly and lightly.

  In the gas compressor according to the present invention, the check valve includes a substantially cylindrical sleeve having at least one end opened and a suction opening communicating with the suction passage on the peripheral wall thereof, and a cylinder inscribed in the sleeve. A valve body which is slidable along the axial direction of the shape and partitions the internal space of the sleeve into two spaces with respect to the axial direction of the sleeve, and a biasing means for biasing the valve body in the opening direction of one end of the sleeve Of the two spaces, the space on the other end side of the sleeve is preferably the space on the compression side in the gas suction operation.

  Here, in the check valve in which the valve body of the check valve is configured to slide in direct contact with the inner wall surface of the suction port, a sleeve as a component of the check valve is provided as a component. In this case, however, the inner wall surface of the suction port on which the valve body abuts and slides fulfills the function of the sleeve, and this inner wall surface also serves as the check valve of the gas compressor according to the present invention. Included in the constituting sleeve.

  According to the gas compressor configured as described above, during the gas non-suction operation, the gas in the gas compressor that has passed through the gas vent passage from the suction passage is caused to act as a back pressure that presses the valve body in the closing direction. And the closed state of the valve body can be firmly held.

  Further, in the gas compressor according to the present invention, the compressor main body includes a cylinder that covers the outside of the outer peripheral surface of the rotating body, two side blocks that sandwich the rotating body from both ends of the rotating body, It is preferable that the main body of the compressor be of a vane rotary type provided with a plurality of vanes that can protrude from the body in the direction of the inner peripheral surface of the cylinder.

  In the vane rotary type gas compressor, since the suction chamber and the discharge chamber are disposed with the compressor interposed therebetween, the problem of pressure loss due to the formation of the suction passage described above becomes significant. Depending on the configuration, the effect of reducing this pressure loss can be made more remarkable.

  According to the gas compressor of the present invention, during the gas suction operation of the check valve, the pressure applied to the gas (refrigerant gas etc.) and the lubricating oil (refrigerator oil etc.) occupying the compression side space of this check valve is Since the relief passage is released to the suction passage through the gas vent passage communicating with the compression side space, the reaction force received by the check valve from the compression side space can be greatly reduced. It can be operated lightly.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, the best embodiment of the gas compressor of the invention will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view of an essential part showing a vane rotary type compressor 100 which is an embodiment of a gas compressor according to the present invention, and FIG. 2 is a case of a cross section taken along line A1-A1 in FIG. 11 is a diagram in which illustration of 11 is omitted.

  The illustrated compressor 100 is used in an air conditioning system mounted on a vehicle, sucks a refrigerant gas G (gas), compresses the refrigerant gas G, and discharges the compressed refrigerant gas G.

  The compressor 100 covers a rotating shaft 51 that rotates by obtaining a driving force from external power, a rotor 50 that rotates around the shaft integrally with the rotating shaft 51, and an outer peripheral surface of the rotor 50. A plurality of cylinders 40, two side blocks (front side block 20 and rear side block 30) that sandwich the rotor 50 from both end surfaces of the rotor 50, and a plurality of cylinders that can project from the rotor 50 toward the inner peripheral surface of the cylinder 40. A compressor body including the vane 58, a suction port 14 that covers the outside of the compressor body, and that sucks the refrigerant gas G from the outside, and a discharge port 16 that discharges the refrigerant gas G to the outside. A formed housing 10 is provided.

  Here, the housing 10 covers a case 11 that wraps substantially the entire compressor body, and an outer side of the front side block 20 side, and an electromagnetic clutch 90 that applies a rotational driving force to the rotary shaft 51 is rotatably attached. The compressor main body is housed in an internal space that includes the front head 12 and is partitioned by the case 11 and the front head 12.

  In addition, with respect to the axial direction of the rotating shaft 51, the refrigerant gas G sucked into the compressor main body by the outer surface of the front side block 20 and the inner surface of the front head 12 is located on the electromagnetic clutch 90 side across the compressor main body. A suction chamber 13 to be introduced is formed, and a high-pressure refrigerant gas discharged from the compressor body by the outer surface of the rear side block 30 and the inner surface of the case 11 on the side opposite to the suction chamber 13 across the compressor body. A discharge chamber 15 in which G temporarily stays is formed.

  An oil separator (such as a wire mesh) 82 that separates the refrigerating machine oil R mixed in the refrigerant gas G discharged from the compressor main body from the refrigerant gas G inside the discharge chamber 15 and on the outer surface of the rear side block 30. The cyclone block 80 provided with is fixed.

  The refrigerating machine oil R separated by the oil separator 82 accumulates at the bottom of the discharge chamber 15, passes through the oil passage 31 drilled from the bottom of the rear side block 30 to the bearing of the rotary shaft 51, and is a bearing portion of the rear side block 30. On the other hand, the bearing portion of the front side block 20 is lubricated through the oil passage 31 of the rear side block 30, the oil passage 46 formed in the cylinder 40, and the oil passage 21 formed in the front side block 20.

  Further, the refrigerating machine oil R that reaches the bearing portions of the front side block 20 and the rear side block 30 and is pumped in the direction of the rotor 50 through a minute gap between the rotary shaft 51 is a vane groove formed in the rotor 50. 56 (see FIG. 2).

  Here, five vane grooves 56 are formed at equal angular intervals in the circumferential direction of the rotor 50, and each vane groove 56 has a width substantially equal to the axial length of the rotor 50. A vane 58 that can project from the outer peripheral surface of the rotor 50 toward the inner peripheral surface 49a of the cylinder 40 is provided.

  A vane back pressure chamber 59 is formed by the end surface of the vane 58 on the center side of the rotor 50 and the wall surface of the vane groove 56, and the refrigerating machine oil R reaching the vane groove 56 applies an internal pressure to the vane back pressure chamber 59. By hanging, the vane 58 protrudes from the outer peripheral surface of the rotor 50 toward the inner peripheral surface 49 a of the cylinder 40.

  Thus, each vane 58 protrudes, and the tip of each vane 58 on the radially outer side of the rotor 50 abuts on the inner peripheral surface 49a of the cylinder 40, whereby the outer peripheral surface of the rotor 50, the inner peripheral surface of the cylinder 40, and The internal space of the compressor body surrounded by the both side blocks 20 and 30 forms five compression chambers 48 whose volumes change as the rotor 50 rotates.

  In FIG. 2, reference numeral 44 denotes a discharge chamber, reference numeral 43 denotes a discharge valve, reference numeral 42 denotes a discharge hole that allows the compression chamber 48 and the discharge chamber 44 in the final stage of the compression stroke to communicate with each other. It is comprised by the valve main body 43a and the valve support 43b. Reference numeral 34 denotes a discharge passage formed in the rear side block 30 for guiding the refrigerant gas G from the discharge chamber 44 to the oil separator 82 formed in the rear side block 30.

  Here, the case 11 of the compressor 100 of the present embodiment is formed with a suction port 14 through which the refrigerant gas G is sucked from the outside and a discharge port 16 through which the refrigerant gas G is discharged to the outside. Both the suction port 14 and the discharge port 16 are provided on the discharge chamber 15 side according to the requirement of the arrangement space and the like. The discharge port 16 is formed on the back side of the suction port 14 in FIG.

  Since the suction port 14 is formed on the discharge chamber 15 side, the suction port 14 and the suction chamber 13 are spaced apart from each other and are not in communication with each other. Is formed in the case 11.

  The suction passage 70 extends substantially in parallel with the axial direction of the rotation shaft, and one end opening thereof opens toward a sleeve 65 of a check valve 60 described later.

  Here, the intake port 14 is provided with a check valve 60 similar to the conventional one shown in FIG. The check valve 60 allows the refrigerant gas G (and mixed refrigeration oil R) to be sucked into the compressor 100 from the outside to the inside, and the refrigerant gas G (and mixed refrigeration oil from the compressor 100 to the outside). R), which has a substantially cylindrical sleeve 65 in which an upper end portion is opened and a suction opening 65a communicating with the suction passage 70 in FIG. A valve body 63 that is slidable along the axial direction of the cylindrical shape and divides the internal space of the sleeve 65 into two spaces with respect to the axial direction of the sleeve 65, and the valve body 63 is opened in the upper end portion opening direction. And a stopper 61 that restricts upward movement of the valve body 63 at the upper end of the sleeve 65, and a bottom that is the other end of the sleeve 65. Hole 65d (opening) is formed in 65b.

  As shown in FIG. 3A, the check valve 60 is configured such that the stopper 61 and the valve body 63 are in contact with each other when the valve body 63 is biased toward the upper end opening side of the sleeve 65. The refrigerant gas G and the refrigerating machine oil R are prevented from being discharged from the suction chamber 13 to the outside of the compressor 100. On the other hand, when the refrigerant gas G is supplied from the outside, due to the pressure balance between the outside and the inside, As shown in FIG. 3B, when the valve body 63 is pushed down against the biasing force of the helical spring 64 and the skirt portion of the valve body 63 descends below the suction opening 65a, the refrigerant gas G from the outside Passes through the suction opening 65 a and is supplied to the suction passage 70.

  Here, the inner space of the sleeve 65 is divided into two upper and lower spaces in the drawing by the valve body 63, and the valve body 63 is displaced during the suction operation of the refrigerant gas G out of these two spaces. The space S1 on the side in which the internal volume is reduced, that is, the direction in which it is lowered in the drawing, is a compression side space in which the internal volume is reduced.

  The case 11 is formed with gas vent passages 71 and 72 that allow the compression-side space S1 and the suction passage 70 to communicate with each other. That is, the upper end portion of the gas vent passage 71 that is drilled from the suction port 14 side and extends coaxially with the suction port 14 communicates with the lower end port 65d of the sleeve 65, while from the lower side of the case 11 in the figure, A gas vent passage 72 that is formed toward the suction passage 70 while communicating with the lower portion of the gas vent passage 71 opens into the suction passage 70.

  In addition, the lower hole of the case 11 formed for drilling the gas vent passage 72 is hermetically closed by a sealing plug 73.

  Next, the operation of the compressor 100 according to this embodiment will be described.

  First, during the non-suction operation of the refrigerant gas G, as shown in FIG. 3A, the valve body 63 is biased to the upper end opening position of the sleeve by the biasing force of the helical spring 64. The valve body 63 and the stopper 61 are in contact with each other with a surface pressure corresponding to the urging force. In this state, the upper end opening of the sleeve 65 is closed by the valve body 63, and the suction opening 65 a of the sleeve 65 that connects the suction passage 70 and the inner space of the sleeve 65 is the side peripheral wall of the valve body 63. The suction port 14 and the suction passage 70 are not communicated with each other because the skirt portion 63a is blocked, and the refrigerant gas G (and the refrigerating machine oil R) inside the compressor 100 flows from the suction passage 70 side to the suction port 14. Prevents backflow.

  At this time, the refrigerant gas G (and the refrigerating machine oil R) inside the compressor 100 flowing into the gas vent passage 72 and the gas vent passage 71 from the suction passage 70 enters the space S1 below the valve body 63 via the port 65d. Since it flows in, it acts also as a pressure which presses the valve body 63 upward, that is, an urging force in a direction in which the check valve 60 is closed. Therefore, the check valve 60 can be reliably held in the closed state.

  On the other hand, in the operating state of the compressor 100, the pressure on the outside of the suction port 14 and the internal pressure of the suction passage 70 leading to the compression chamber 48 across the check valve 60 due to the change in the volume of the compression chamber 48 of the compressor body. , The valve body 63 is displaced downward in the figure against the biasing force of the helical spring 64.

  When the valve body 63 is pushed down from the upper edge of the suction opening 65 a of the sleeve 65, the suction port 14 and the suction passage 70 communicate with each other, and the refrigerant gas G (and the refrigerant gas G) flows from the suction port 14 to the suction passage 70. At the same time, the refrigerating machine oil R) circulated in the system flows in, and the refrigerant gas G is supplied to the suction chamber 13.

  During the suction operation of the check valve 60, the space S 1 below the valve body 63 in the inner space of the sleeve 65 is compressed into the space on the compression side (the compression side space of the check valve). However, since the compression-side space S1 communicates with the suction passage 70 through the hole 65d at the lower end of the sleeve 65 and the gas vent passages 71 and 72, the refrigerant occupying the compression-side space S1. The gas G ′ or the like is released to the suction passage 70 through the gas vent passages 71 and 72.

  Therefore, as in a compressor in which the compression side space S1 is sealed (for example, the compressor 100 shown in FIG. 6), the pressure of the refrigerant gas G ′ occupying the compression side space S1 Descent is not suppressed. Therefore, the check valve 60 can be opened smoothly and lightly.

  Note that the operation of the compressor 100 after the refrigerant gas G is supplied to the suction chamber 13 from the suction port 14 via the check valve 60 and the suction passage 70 is a conventional gas compressor (for example, as shown in FIG. 4). The operation is similar to that of the compressor 100), and the operation of the compressor 100 shown in FIG.

  As described above, according to the compressor 100 according to this embodiment, the check valve 60 can be opened smoothly and lightly.

  Further, the compressor 100 according to the present embodiment includes a substantially cylindrical sleeve 65 in which the check valve 60 is substantially open at both ends and has a suction opening 65a communicating with the suction passage 70 on its peripheral wall, and a sleeve A valve body 63 that is inscribed in the axial direction of the cylinder 65 and that is slidable along the axial direction of the cylinder 65 and divides the internal space of the sleeve 65 into two spaces with respect to the axial direction of the sleeve 65, and the valve body 63 at the upper end of the sleeve 65. Since the helical spring 64 biased in the opening direction is provided and the space S1 on the hole 65d side of the malleable portion of the sleeve 65 is the space on the compression side in the refrigerant gas G suction operation. During the non-suction operation of the refrigerant gas G, the refrigerant gas G that has passed through the degassing passages 71 and 72 from the suction passage 70 can act as a back pressure that presses the valve body 63 in the closing direction. It is possible to maintain the closed state firmly.

  In the compressor 100 of the present embodiment, the compressor body includes a cylinder 40 that covers the outside of the outer peripheral surface of the rotor 50, and two side blocks 20 and 30 that sandwich the rotor 50 from both ends of the rotor 50, respectively. The gas compressor is a vane rotary type that includes a plurality of vanes 58 that can project from the rotor 50 toward the inner peripheral surface of the cylinder 40. However, the gas compressor according to the present invention is limited to this configuration. Instead, a scroll-type gas compressor or the like may be used.

It is sectional drawing which shows the vane rotary type compressor which is one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing which shows the cross section along the A1-A1 line of the compressor shown in FIG. It is a principal part enlarged view explaining operation | movement of the check valve of the compressor shown in FIG. It is a figure which shows the conventional gas compressor (compressor), (a) shows a longitudinal section, (b) shows sectional drawing along the A2-A2 line in (a). It is a principal part enlarged view explaining operation | movement of the check valve of the compressor shown in FIG. It is a longitudinal cross-sectional view which shows the compressor in which the suction port was provided in the discharge chamber side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Housing 11 Case 12 Front head 13 Suction chamber 14 Suction port 15 Discharge chamber 16 Discharge port 20 Front side block 30 Rear side block 40 Cylinder 50 Rotor 51 Rotating shaft 60 Check valve 61 Stopper 63 Valve body 63a Skirt portion 64 Energizing means)
65 Sleeve 65a Suction opening 70 Suction passage 71 Gas vent hole (vertical part)
72 Degassing hole (inclined part)
73 Plug G Refrigerant gas R Refrigerating machine oil S1 Compression side space

Claims (3)

A compressor body having a rotating body that rotates about a rotation axis, a housing that covers the outside of the compressor body, and that is formed with a suction port for sucking gas from the outside and a discharge port for discharging gas to the outside; A suction chamber that communicates with the suction port and into which the gas sucked into the compressor body is introduced, and a discharge that communicates with the discharge port and stores the gas discharged from the compressor body. A chamber is formed across the compressor body with respect to the axial direction of the rotating shaft, and the suction port allows the suction of gas from the outside to the inside and prevents the backflow of gas from the inside to the outside. In a gas compressor provided with a check valve,
The suction port is formed on the discharge chamber side with respect to the axial direction, a suction passage is formed in the housing to connect the suction port and the suction chamber, and the check valve is compressed in the gas suction operation. A gas compressor characterized in that a gas vent passage for communicating the space on the side and the suction passage is formed in the housing.   The check valve includes a substantially cylindrical sleeve having an opening at least at one end and a suction opening communicating with the suction passage on a peripheral wall thereof, and is slid along the axial direction of the cylinder inscribed in the sleeve. A valve body that is movable and partitions the internal space of the sleeve into two spaces in the axial direction of the sleeve; and a biasing means that biases the valve body in the opening direction of one end of the sleeve, 2. The gas compressor according to claim 1, wherein a space on the other end side of the sleeve among the two spaces is a space on the compression side in the gas suction operation. The compressor main body includes a cylinder that covers the outer peripheral surface of the rotating body, two side blocks that sandwich the rotating body from both end surface sides of the rotating body, and an inner periphery of the cylinder from the rotating body. 3. The gas compressor according to claim 1, wherein the gas compressor is a vane rotary type compressor body including a plurality of vanes that can project in a plane direction. 4.

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